WO1995023717A1 - Electromagnetic valve, in particular for slip-controlled motor vehicle braking systems - Google Patents

Electromagnetic valve, in particular for slip-controlled motor vehicle braking systems Download PDF

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Publication number
WO1995023717A1
WO1995023717A1 PCT/EP1995/000137 EP9500137W WO9523717A1 WO 1995023717 A1 WO1995023717 A1 WO 1995023717A1 EP 9500137 W EP9500137 W EP 9500137W WO 9523717 A1 WO9523717 A1 WO 9523717A1
Authority
WO
WIPO (PCT)
Prior art keywords
valve
sleeve
magnet armature
armature
piston
Prior art date
Application number
PCT/EP1995/000137
Other languages
German (de)
French (fr)
Inventor
Karl Heinz MÜLLER
Original Assignee
Itt Automotive Europe Gmbh
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Itt Automotive Europe Gmbh filed Critical Itt Automotive Europe Gmbh
Publication of WO1995023717A1 publication Critical patent/WO1995023717A1/en

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
    • B60T8/00—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force
    • B60T8/32—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration
    • B60T8/34—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition
    • B60T8/36—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition including a pilot valve responding to an electromagnetic force
    • B60T8/3615—Electromagnetic valves specially adapted for anti-lock brake and traction control systems
    • B60T8/363—Electromagnetic valves specially adapted for anti-lock brake and traction control systems in hydraulic systems
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
    • B60T8/00—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force
    • B60T8/32—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration
    • B60T8/34—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition
    • B60T8/36—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition including a pilot valve responding to an electromagnetic force
    • B60T8/3615—Electromagnetic valves specially adapted for anti-lock brake and traction control systems
    • B60T8/363—Electromagnetic valves specially adapted for anti-lock brake and traction control systems in hydraulic systems
    • B60T8/365—Electromagnetic valves specially adapted for anti-lock brake and traction control systems in hydraulic systems combining a plurality of functions in one unit, e.g. pressure relief
    • H—ELECTRICITY
    • H01—ELECTRIC ELEMENTS
    • H01F—MAGNETS; INDUCTANCES; TRANSFORMERS; SELECTION OF MATERIALS FOR THEIR MAGNETIC PROPERTIES
    • H01F7/00—Magnets
    • H01F7/06—Electromagnets; Actuators including electromagnets
    • H01F7/08—Electromagnets; Actuators including electromagnets with armatures
    • H01F7/088—Electromagnets; Actuators including electromagnets with armatures provided with means for absorbing shocks

Definitions

  • Solenoid valve in particular for slip-controlled motor vehicle brake systems
  • the invention relates to an electromagnetic valve, in particular for slip-controlled motor vehicle brake systems according to the preamble of claim 1.
  • the invention is based on the object of designing the electromagnetic valve resulting from the aforementioned prior art in such a way that the noises which occur when the electromagnetic valve is actuated are damped.
  • the magnet armature movement is damped hydraulically, whereby valve noises are considerably reduced both when the valve closing member is placed on the valve seat and when it is placed on the end face of the magnet armature facing away from the valve closing member on the valve housing.
  • pressure waves of the fluid and the associated flow noises are reduced by actuating the valve.
  • the aperture effect of the damping device can be selected so that no noticeable response Solenoid valve delay occurs.
  • the diaphragm function can be designed as a narrow annular gap between the diaphragm piston and the valve housing. This results in a very simple construction of the damping device.
  • the orifice piston attached to the magnetic armature is designed as a stepped piston, so that the annular surface of the step is attached to an intermediate part fixed to the housing, which is placed on the sleeve, or on Valve closure of the valve housing can be hydraulically damped.
  • FIG. 1 shows a solenoid valve closed in the basic position, with a particularly compact arrangement of the noise damping device
  • FIG. 2 shows an electromagnetic valve which is open in the basic position, with a further embodiment variant for noise damping
  • FIG. 3 shows a solenoid valve which is open when de-energized and has a particularly simple noise damping device
  • Figure 4 shows another embodiment of a normally open solenoid valve with a damping device.
  • the electromagnetic valve shown in FIG. 1 has a valve housing 2 with a chamber 3.
  • a sleeve 12 and a magnet coil 4 are fixed to the housing and a magnet armature 5 is axially displaceably mounted within the sleeve 12.
  • a valve tappet is fastened with a valve closing member 11, which is loaded within the sleeve 12 by a return spring 7, which rests in a bore of the valve closure receiving the magnetic core 1 supports.
  • the solenoid valve is consequently designed as a closed valve in the electromagnetically non-energized basic position, which consequently, with its valve closing member 11 on the valve seat 13, separates an inlet channel 14 and an outlet channel 15.
  • a relatively simple to manufacture orifice piston 17 is screwed onto the side of the magnet armature 5 facing away from the valve closing member 11. Between the diaphragm piston 17 and the wall surrounding it and the sleeve 12 there is an annular gap 19 which is designed with a small passage and which effects the diaphragm function.
  • the orifice piston 17 divides the magnet armature chamber (chamber 3) into two chamber parts which contain a fluid and are connected to one another via the annular gap 19.
  • a further modification of the invention can consist in that the orifice piston 17 is fastened to the magnet armature 5 with a clamp or latching connection, or is made in one piece with the magnet armature 5.
  • one or more aperture bores can be provided in the aperture piston 17, which connect the two chamber parts delimited by the magnet armature 5.
  • the diaphragm piston 17 can also be provided in solenoid valves that are closed by energizing the solenoids.
  • FIG. 2 therefore shows, based on the basic structure of an electromagnetic valve described in FIG. 1, alternatively an electromagnetic valve which is open in the electromagnetically non-energized basic position and which receives the magnetic core 1 in the lower region of its valve housing 2.
  • the magnetic armature 5 On which the orifice piston 17 also takes over the function of an end position part in order to ensure effective noise reduction in both stroke directions.
  • the orifice piston 17 is designed as a stepped piston, which has an annular gap 19 with respect to an intermediate part 8 integrated in the closure region of the valve housing 2 and adapted to the shape of the piston step.
  • FIG. 3 shows, in deviation from the basic structure of the electromagnetically open solenoid valve in FIG. 2, a simplified embodiment of the orifice piston 17 as a stepless stop piston, so that the hydraulic damper effect by displacing the pressure medium volume compressed above the orifice piston 17 via the annular gap 19 in the lower region of the chamber 3 is only effective when the armature 5 is moved into its non-excited basic position.
  • This is a particularly simple to implement solution for noise reduction, in which the annular gap 19 on the orifice piston 17 and the stop damping of the orifice piston on the valve housing 2 are also effective.
  • the diaphragm piston 17 is also fastened to the magnet armature 5 in a force-locking manner by means of retaining screws 10 on the magnet armature 5.
  • Other types of fastening for example using snap-in and clip connections, can be used.
  • FIG. 4 shows a special construction of the sleeve 12 receiving the armature 5.
  • the sleeve 12 is produced as a thin-walled deep-drawn part in the form of a valve dome closed at one end and with its end section facing away from the valve dome for insertion and loading. fix the magnet armature 5 and the associated adjusting device open conically.
  • the likewise conically tapered magnetic core 1 closes the end section of the sleeve 12 and forms the support of the sleeve 12, which, by caulking the valve carrier material on the conical end section of the sleeve 12, essentially provides a force-fitting fastening of the magnetic core 1 and the sleeve 12 in the ven ⁇ valve housing 2 ensures.
  • a rotationally symmetrical filler in the valve dome represents a further end position part 16 for the application of the magnet armature 5, which at the same time is designed as a deformation element which is compressed after the stroke of the magnet armature 5 has been set.
  • the filler body is precisely fixed in its position from the outside by lancings 18 on the sleeve 12 above the magnet armature 5, so that it can absorb hydrodynamic alternating forces.
  • the section of the magnet armature 5 facing the filler body is designed as a diaphragm piston, so that a defined annular gap 19 remains at the upper section of the magnet core 1, through which a pressure medium exchange between the pressure spaces above occurs during a stroke movement and takes place below the magnet armature 5.
  • the plane-parallel end faces of the filler body and the magnet armature 5 come to a stop (end position).
  • this embodiment enables simple attachment and use of the end position part 16 (filler body) for valve stroke adjustment.
  • the end position part 16 is designed to be correspondingly voluminous in order to keep the cavity in the valve dome which determines the damping effect as small as possible and by appropriate to bring about a sound-absorbing measure, whereby mechanical and hydraulic forces can also be absorbed by the appropriate rigidity and strength.
  • FIG. 4 the alternative embodiments from FIGS. 1 to 3 can also be transferred to the orifice piston 17, so that the construction shown in FIG. 4 only shows one variant of the embodiment variants from FIGS. 1 to 3.

Abstract

The invention relates to an electromagnetic valve having a valve housing (2) which comprises a plurality of valve components, such as a valve closure member (11), mounted on the valve tappet (6), and an armature (5), the valve components adapted for the function of the electromagnetic valve. The valve closure member (11) can be applied against a valve seat and the armature (5) can be applied against a magnet core (1). The electromagnetic valve further has a sleeve (12), which is held at the magnet core (1) and in which the armature (5) is guided such that it is axially movable, and a magnet coil (4) which surrounds the periphery of the sleeve (12) and can close or open the pressure medium connection between at least one pressure medium inlet duct (14) and a pressure medium outlet duct (15) in the valve housing (2) by means of the switching position of the valve closure member (11). Disposed between the armature (5) and the sleeve (12) in the valve housing (2) is an axially movable diaphragm piston (17) which has a clearance which is less than the clearance between the armature (5) and the sleeve (12).

Description

Elektromagnetventil, insbesondere für schlupfgeregelte KraftfahrzeugbremsanlagenSolenoid valve, in particular for slip-controlled motor vehicle brake systems
Die Erfindung bezieht sich auf ein Elektromagnetventil, insbesondere für schlupfgeregelte Kraftfahrzeugbremsanlagen nach dem Oberbegriff des Anspruchs 1.The invention relates to an electromagnetic valve, in particular for slip-controlled motor vehicle brake systems according to the preamble of claim 1.
Bei einem bekannten Magnetventil dieser ArtIn a known solenoid valve of this type
(DE 41 41 546 AI) treten beim Übergang des Ankers in die eine oder andere Endlage unter anderem Anschlaggeräusche auf.(DE 41 41 546 AI) occur at the transition of the armature into one or the other end position, inter alia, stop noises.
Der Erfindung liegt die Aufgabe zugrunde, das aus dem vor¬ genannten Stand der Technik hervorgegangene Elektromagnet- ventil so auszubilden, daß die bei der Betätigung des Elek¬ tromagnetventils auftretenden Geräusche gedämpft sind.The invention is based on the object of designing the electromagnetic valve resulting from the aforementioned prior art in such a way that the noises which occur when the electromagnetic valve is actuated are damped.
Erfindungsgemäß ist diese Aufgabe durch die kennzeichnenden Merkmale des Patentanspruchs 1 gelöst, wonach zwischen dem Magnetanker und der Hülse im Ventilgehäuse ein axial beweg¬ licher Blendenkolben angeordnet ist, der ein Spiel auf¬ weist, das kleiner ist als das zwischen dem Magnetanker und der Ventilhülse bestehende Spiel.According to the invention, this object is achieved by the characterizing features of patent claim 1, according to which an axially movable orifice piston is arranged between the magnet armature and the sleeve in the valve housing and has a play which is smaller than that existing between the magnet armature and the valve sleeve Game.
Bei dieser Ausbildung wird die Magnetankerbewegung hydrau¬ lisch gedämpft, wodurch Ventilgeräusche sowohl beim Anlegen des Ventilschließgliedes am Ventilsitz, wie auch beim Anle¬ gen an der vom Ventilschließglied abgewandten Stirnfläche des Magnetankers am Ventilgehäuse erheblich reduziert sind. Desgleichen werden durch das Betätigen des Ventils Druck¬ wellen des Fluids und die damit verbundenen Strömungsgeräu- sche gemindert. Die Blendenwirkung der Dämpfungseinrichtung läßt sich so wählen, daß dennoch keine merkliche Ansprech- Verzögerung des Magnetventils auftritt. Dadurch, daß der Magnetanker den Blendenkolben und bei Bedarf auch die Funktion des Endlagenteils aufweist, ergibt sich eine kom¬ pakte Bauweise, wobei der Blendenkolben gleichzeitig zur Führung des Ankers dient.In this embodiment, the magnet armature movement is damped hydraulically, whereby valve noises are considerably reduced both when the valve closing member is placed on the valve seat and when it is placed on the end face of the magnet armature facing away from the valve closing member on the valve housing. Likewise, pressure waves of the fluid and the associated flow noises are reduced by actuating the valve. The aperture effect of the damping device can be selected so that no noticeable response Solenoid valve delay occurs. The fact that the magnet armature has the orifice piston and, if necessary, also the function of the end position part results in a compact construction, the orifice piston simultaneously serving to guide the armature.
Die Blendenfunktion kann als enger Ringspalt zwischen dem Blendenkolben und dem Ventilgehäuse ausgebildet sein. Dies ergibt eine sehr einfache Konstruktion der Dämpfungsein¬ richtung.The diaphragm function can be designed as a narrow annular gap between the diaphragm piston and the valve housing. This results in a very simple construction of the damping device.
Die Endlagendämpfung des Magnetankers am gehäusefesten An¬ schlag, wie auch die Befestigung des als Anschlagteils wirksamen Blendenkolbens am Magnetanker geschieht zweck¬ mäßig durch planparallele, koaxiale Ausrichtung der plat- tenförmigen Anschlagkörper, so daß eine besonders kompakte, leicht herzustellende Baugruppe gebildet ist.The end position damping of the magnet armature on the stop fixed to the housing, as well as the attachment of the diaphragm piston acting as a stop part to the magnet armature, are expediently carried out by plane-parallel, coaxial alignment of the plate-shaped stop bodies, so that a particularly compact, easy-to-manufacture assembly is formed.
Vorteilhaft ist es, den Blendenkolben als separates Teil auszuführen und mit dem Magnetanker lösbar zu verbinden. Hierdurch ist eine beliebige, bedarfsgerechte Auswahl und Anordnung einzelner Module auf einfache Weise möglich.It is advantageous to design the orifice piston as a separate part and to detachably connect it to the magnet armature. In this way, any desired, needs-based selection and arrangement of individual modules is possible in a simple manner.
Um den Blendenkolben in beiden Ankerhubrichtungen als An¬ schlagdämpfer wirksam werden zu lassen, ist der am Magnet¬ anker befestigte Blendenkolben als Stufenkolben ausgeführt, so daß die .Ringfläche der Stufe an einem gehäusefesten Zwi¬ schenteil, das auf der Hülse aufgesetzt ist, oder am Ven¬ tilverschluß des Ventilgehäuses hydraulisch gedämpft anlie¬ gen kann.In order to allow the orifice piston to act as a stop damper in both armature stroke directions, the orifice piston attached to the magnetic armature is designed as a stepped piston, so that the annular surface of the step is attached to an intermediate part fixed to the housing, which is placed on the sleeve, or on Valve closure of the valve housing can be hydraulically damped.
Um gleichzeitig die Ankerhubeinstellung und die Reaktions¬ fläche für den Blendenkolben zu bewerkstelligen, eignet sich die Anordnung eines in der Hülse fixierten Endlagen¬ teils.In order to simultaneously accomplish the armature stroke adjustment and the reaction surface for the orifice piston, it is suitable the arrangement of an end position part fixed in the sleeve.
Weitere Merkmale, Vorteile und -Anwendungsmöglichkeiten ge¬ hen aus der nachfolgenden Beschreibung mehrerer Auführungs- beispiele hervor.Further features, advantages and possible uses emerge from the following description of several exemplary embodiments.
Es zeigen:Show it:
Figur 1 ein in der Grundstellung geschlossenes Elektro¬ magnetventil, mit einer besonders kompakten Anord¬ nung der Geräuschdämpfungseinrichtung,1 shows a solenoid valve closed in the basic position, with a particularly compact arrangement of the noise damping device, FIG.
Figur 2 ein in der Grundstellung geöffnetes Elektromagnet- ventil, mit einer weiteren AusführungsVariante zur Geräuschdämpfung,FIG. 2 shows an electromagnetic valve which is open in the basic position, with a further embodiment variant for noise damping,
Figur 3 ein stromlos offen geschaltetes Elektromagnetven¬ til mit einer besonders einfachen Geräusch¬ dämpfungseinrichtung,FIG. 3 shows a solenoid valve which is open when de-energized and has a particularly simple noise damping device,
Figur 4 eine weitere Ausführungsform eines stromlos offen geschalteten Elektromagnetventils mit einer Dämpfungseinrichtung.Figure 4 shows another embodiment of a normally open solenoid valve with a damping device.
Das in Figur 1 dargestellte Elektromagnetventil hat ein Ventilgehäuse 2 mit einer Kammer 3. In der Kammer 3 ist ei¬ ne Hülse 12 und eine Magnetspule 4 gehäusefest und ein Magnetanker 5 innerhalb der Hülse 12 axial verschiebbar ge¬ lagert. Am Magnetanker 5 ist ein Ventilstößel mit einem Ventilschließglied 11 befestigt, der innerhalb der Hülse 12 von einer Rückstellfeder 7 belastet ist, die sich in einer Bohrung des den Magnetkern 1 aufnehmenden Ventilverschluß abstützt. Das Elektromagnetventil ist demzufolge als ein in der elektromagnetisch nicht erregten Grundstellung ge¬ schlossenes Ventil ausgebildet, das folglich mit seinem Ventilschließglied 11 am Ventilsitz 13 einen Einlaßkanal 14 und einen Auslaßkanal 15 trennt.The electromagnetic valve shown in FIG. 1 has a valve housing 2 with a chamber 3. In the chamber 3, a sleeve 12 and a magnet coil 4 are fixed to the housing and a magnet armature 5 is axially displaceably mounted within the sleeve 12. On the magnet armature 5, a valve tappet is fastened with a valve closing member 11, which is loaded within the sleeve 12 by a return spring 7, which rests in a bore of the valve closure receiving the magnetic core 1 supports. The solenoid valve is consequently designed as a closed valve in the electromagnetically non-energized basic position, which consequently, with its valve closing member 11 on the valve seat 13, separates an inlet channel 14 and an outlet channel 15.
Auf der dem Ventilschließglied 11 abgekehrten Seite des Magnetankers 5 ist ein relativ einfach herzustellender Blendenkolben 17 aufgeschraubt. Zwischen dem Blendenkolben 17 und der ihn umgebenden Wand und der Hülse 12 ist ein mit kleinem Durchlaß ausgebildeter Ringspalt 19 vorgesehen, der die Blendenfunktion bewirkt.A relatively simple to manufacture orifice piston 17 is screwed onto the side of the magnet armature 5 facing away from the valve closing member 11. Between the diaphragm piston 17 and the wall surrounding it and the sleeve 12 there is an annular gap 19 which is designed with a small passage and which effects the diaphragm function.
Der Blendenkolben 17 unterteilt den Magnetankerraum (Kammer 3) in zwei Kammerteile, die ein Fluid enthalten und über den Ringspalt 19 miteinander verbunden sind.The orifice piston 17 divides the magnet armature chamber (chamber 3) into two chamber parts which contain a fluid and are connected to one another via the annular gap 19.
Beim Einschalten (Erregen) der Magnetspule 4 wird der Magnetanker 5 entgegen der Kraft der Rückstellfeder 7 in die Magnetspule 7 hineingezogen, bis das Ventilschließglied 11 vom Ventilsitz 13 abhebt und den Durchlaß des Fluids vom Eingangskanal 14 zum Ausgangskanal 15 (oder umgekehrt) freigibt. Dabei wird das Fluid durch den Blendenkolben 17 aus dem oberen Kammerteil über den Ringspalt 19 in den un¬ teren Kammerteil verdrängt und die Bewegung des Magnetan¬ kers 15 verlangsamt. Hierdurch wird das Geräusch beim Anle¬ gen des Blendenkolbens 17 am Magnetkern 1 gedämpft.When the solenoid 4 is switched on (energized), the magnet armature 5 is drawn into the solenoid 7 against the force of the return spring 7 until the valve closing member 11 lifts off the valve seat 13 and releases the passage of the fluid from the inlet channel 14 to the outlet channel 15 (or vice versa). The fluid is displaced by the orifice piston 17 from the upper chamber part via the annular gap 19 into the lower chamber part and the movement of the magnet armature 15 is slowed down. This dampens the noise when the diaphragm piston 17 is placed against the magnetic core 1.
Eine weitere Abwandlung der Erfindung kann darin bestehen, daß der Blendenkolben 17 mit einer Klemm- bzw. Rastverbin¬ dung am Magnetanker 5 befestigt ist, oder einstückig mit dem Magnetanker 5 ausgeführt ist. Durch die gezeigte lösba¬ re Verbindungstechnik des Blendenkolbens 17 mit dem Magnet- anker 5 ist jederzeit ein zerstörungsfreier Montageeingriff und kostengünstiger Austausch der Einzelelemente sicherge¬ stellt, wobei Blendenkolben 17 mit unterschiedlicher Blen¬ dencharakteristik die jeweils gewünschte Ventilabstimmung ermöglichen, ohne das gesamte Ventil oder Ventilbauguppen tauschen zu müssen.A further modification of the invention can consist in that the orifice piston 17 is fastened to the magnet armature 5 with a clamp or latching connection, or is made in one piece with the magnet armature 5. Through the shown releasable connection technology of the orifice piston 17 with the magnet Anchor 5 ensures non-destructive assembly intervention and cost-effective replacement of the individual elements at any time, with orifice pistons 17 with different orifice characteristics enabling the desired valve tuning in each case without having to replace the entire valve or valve assemblies.
Statt des Ringspalts 19 oder auch zusätzlich zum Ringspalt 19, kann eine oder mehrere Blendenbohrungen im Blendenkol¬ ben 17 vorgesehen sein, die die beiden durch den Magnetan¬ ker 5 begrenzten Kammerteile verbinden.Instead of the annular gap 19 or also in addition to the annular gap 19, one or more aperture bores can be provided in the aperture piston 17, which connect the two chamber parts delimited by the magnet armature 5.
Statt bei einem Elektromagnetventil, das durch Einschalten der Magnetspule geöffnet wird, kann der Blendenkolben 17 auch bei Magnetventilen vorgesehen sein, die durch das Er¬ regen der Magnetspulen geschlossen werden.Instead of an electromagnetic valve that is opened by switching on the solenoid, the diaphragm piston 17 can also be provided in solenoid valves that are closed by energizing the solenoids.
Die Figur 2 zeigt daher in Anlehnung an den in Figur 1 be¬ schriebenen prinzipiellen Aufbau eines Elektromagnetven¬ tils, alternativ ein in der elektromagnetisch nicht erreg¬ ten Grundstellung geöffnetes Elektromagnetventil, das im unteren Bereich seines Ventilgehäuses 2 den Magnetkern 1 aufnimmt. Oberhalb des Magnetkerns 1 steht der Magnetanker 5 über, auf dem der Blendenkolben 17 zusätzlich die Funk¬ tion eines Endlagenteils übernimmt, um eine wirkungsvolle Geräuschreduzierung in beiden Hubrichtungen zu gewähr¬ leisten. Der Blendenkolben 17 ist hierzu als Stufenkolben ausgeführt, der gegenüber einem im Verschlußbereich des Ventilgehäuses 2 integrierten, an die Form der Kolbenstufe angepaßten Zwischenteil 8 einen Ringspalt 19 aufweist. Un¬ abhängig von der Hubbewegung des Magnetankers 5 erfolgt ei¬ ne Verdrängerwirkung des Fluids im Ringspalt 19, die infol¬ ge der Kolbenstufe zu einer doppelten Umlenkung des Druck- mittelstroms im Strömungsspalt führt und die somit hydrau¬ lisch in beiden Bewegungsrichtungen eine Anschlagdämpfung bewirkt. Zwischen dem Blendenkolben 17 und dem Magnetanker 5 befindet sich eine Distanzscheibe 9 zur exakten Hubein¬ stellung des Magnetankers 5. Die Befestigung des Blenden¬ kolbens 17 mit der Distanzscheibe 9 am Magnetanker 5 voll¬ zieht sich im Ausführungsbeispiel mittels Halteschrauben 10. Die offene Grundstellung des Ventilschließgliedes 11 ist durch eine zwischen dem Magnetkern 1 und dem Magnetan¬ ker 5 eingespannte Rückstellfeder 7 realisiert.FIG. 2 therefore shows, based on the basic structure of an electromagnetic valve described in FIG. 1, alternatively an electromagnetic valve which is open in the electromagnetically non-energized basic position and which receives the magnetic core 1 in the lower region of its valve housing 2. Above the magnetic core 1 there is the magnetic armature 5, on which the orifice piston 17 also takes over the function of an end position part in order to ensure effective noise reduction in both stroke directions. For this purpose, the orifice piston 17 is designed as a stepped piston, which has an annular gap 19 with respect to an intermediate part 8 integrated in the closure region of the valve housing 2 and adapted to the shape of the piston step. Irrespective of the stroke movement of the magnet armature 5, there is a displacement effect of the fluid in the annular gap 19, which as a result of the piston stage leads to a double deflection of the pressure leads medium flow in the flow gap and thus hydraulically causes a stop damping in both directions of movement. Between the orifice piston 17 and the magnet armature 5 there is a spacer 9 for exact stroke adjustment of the magnet armature 5. The attachment of the orifice piston 17 with the spacer 9 to the magnet armature 5 is accomplished in the exemplary embodiment by means of retaining screws 10. The open basic position of the Valve closing member 11 is realized by a return spring 7 clamped between the magnet core 1 and the magnet armature 5.
Die Figur 3 zeigt abweichend vom Grundaufbau des stromlos offen geschalteten Elektromagnetventils in Figur 2, eine vereinfachte Ausführung des Blendenkolbens 17 als stufenlo¬ ser Anschlagkolben, so daß die hydraulische Dämpferwirkung durch Verdrängung des oberhalb zum Blendenkolben 17 kompri¬ mierten Druckmittelvolumens über den Ringspalt 19 in den unteren Bereich der Kammer 3 nur bei einer Hubbewegung des Magnetankers 5 in seine nicht erregte Grundstellung wirksam ist. Dies ist eine besonders einfach zu realisierende Lö¬ sung für die Geräuschminderung, bei der gleichfalls der Ringspalt 19 am Blendenkolben 17 und die Anschlagdämpfung des Blendenkolbens am Ventilgehäuse 2 wirksam sind. Die Be¬ festigung des Blendenkolbens 17 am Magnetanker 5 erfolgt gleichfalls kraftschlüssig mittels Halteschrauben 10 am Magnetanker 5. Andere Befestigungsarten, beispielsweise durch Rast- und Clipverbindungen sind anwendbar.3 shows, in deviation from the basic structure of the electromagnetically open solenoid valve in FIG. 2, a simplified embodiment of the orifice piston 17 as a stepless stop piston, so that the hydraulic damper effect by displacing the pressure medium volume compressed above the orifice piston 17 via the annular gap 19 in the lower region of the chamber 3 is only effective when the armature 5 is moved into its non-excited basic position. This is a particularly simple to implement solution for noise reduction, in which the annular gap 19 on the orifice piston 17 and the stop damping of the orifice piston on the valve housing 2 are also effective. The diaphragm piston 17 is also fastened to the magnet armature 5 in a force-locking manner by means of retaining screws 10 on the magnet armature 5. Other types of fastening, for example using snap-in and clip connections, can be used.
In der Figur 4 ist eine spezielle Konstruktion der den Magnetanker 5 aufnehmenden Hülse 12 angegeben. Die Hülse 12 ist als dünnwandiges Tiefziehteil in Form eines am einen Ende geschlossenen Ventildoms hergestellt und mit ihrer dem Ventildom abgewandten Endabschnitt zum Einfügen und Be- festigen des Magnetankers 5 sowie der zugehörigen Justier¬ einrichtung kegelförmig geöffnet. Der gleichfalls kegelför¬ mig verjüngte Magnetkern 1 verschließt den Endabschnitt der Hülse 12 und bildet die Abstützung der Hülse 12, die durch eine Verstemmung des Ventilträgermaterials am kegelförmigen Endabschnitt der Hülse 12 im wesentlichen eine kraftschlüs¬ sige Befestigung des Magnetkerns 1 und der Hülse 12 im Ven¬ tilgehäuse 2 sicherstellt. Ein rotationssymmetrischer Füll¬ körper im Ventildom stellt ein weiteres Endlagenteil 16 für das Anlegen des Magnetankers 5 dar, das gleichzeitig als Deformationselement ausgebildet ist, welches nach erfolgter Hubeinstellung des Magnetankers 5 gestaucht ist. Der Füll¬ körper ist von außen durch Lancierungen 18 an der Hülse 12 oberhalb des Magnetankers 5 in seiner Lage exakt fixiert, so daß er hydrodynamische Wechselkräfte aufnehmen kann. Zur Realisierung der Blendenfunktion ist der dem Füllkörper zu¬ gewandte Abschnitt des Magnetanker 5 als Blendenkolben aus¬ gebildet, so daß ein definierter Ringspalt 19 am oberen Ab¬ schnitt des Magnetkerns 1 verbleibt, durch den bei einer Hubbewegung ein Druckmittelaustausch zwischen den Druckräu¬ men oberhalb und unterhalb des Magnetankers 5 erfolgt. So¬ fern das oberhalb des Magnetankers 5 befindliche Fluid aus dem Druckraum verdrängt ist, gelangen die planparallelen Stirnflächen des Füllkörpers und des Magnetankers 5 auf An¬ schlag (Endlage).FIG. 4 shows a special construction of the sleeve 12 receiving the armature 5. The sleeve 12 is produced as a thin-walled deep-drawn part in the form of a valve dome closed at one end and with its end section facing away from the valve dome for insertion and loading. fix the magnet armature 5 and the associated adjusting device open conically. The likewise conically tapered magnetic core 1 closes the end section of the sleeve 12 and forms the support of the sleeve 12, which, by caulking the valve carrier material on the conical end section of the sleeve 12, essentially provides a force-fitting fastening of the magnetic core 1 and the sleeve 12 in the ven ¬ valve housing 2 ensures. A rotationally symmetrical filler in the valve dome represents a further end position part 16 for the application of the magnet armature 5, which at the same time is designed as a deformation element which is compressed after the stroke of the magnet armature 5 has been set. The filler body is precisely fixed in its position from the outside by lancings 18 on the sleeve 12 above the magnet armature 5, so that it can absorb hydrodynamic alternating forces. To implement the diaphragm function, the section of the magnet armature 5 facing the filler body is designed as a diaphragm piston, so that a defined annular gap 19 remains at the upper section of the magnet core 1, through which a pressure medium exchange between the pressure spaces above occurs during a stroke movement and takes place below the magnet armature 5. Insofar as the fluid located above the magnet armature 5 is displaced from the pressure chamber, the plane-parallel end faces of the filler body and the magnet armature 5 come to a stop (end position).
Diese Ausführungsform ermöglicht außer den in den vorange¬ gangenen Ausführungsbeispielen beschriebenen hydraulischen Dämpferprinzip eine einfache Befestigung und Nutzung des Endlagenteils 16 (Füllkörpers) zur Ventilhubeinstellung. Das Endlagenteil 16 ist entsprechend voluminös gestaltet, um den die Dämpferwirkung bestimmenden Hohlraum im Ventil¬ dom möglichst klein zu halten und durch entsprechende Ei- genmasse eine schallschluckende Maßnahme herbeizuführen, wobei durch die entsprechende Steifigkeit und Festigkeit auch mechanische sowie hydraulische Kräfte gut aufgenommen werden können.In addition to the hydraulic damper principle described in the preceding exemplary embodiments, this embodiment enables simple attachment and use of the end position part 16 (filler body) for valve stroke adjustment. The end position part 16 is designed to be correspondingly voluminous in order to keep the cavity in the valve dome which determines the damping effect as small as possible and by appropriate to bring about a sound-absorbing measure, whereby mechanical and hydraulic forces can also be absorbed by the appropriate rigidity and strength.
Auf figur 4 sind gleichfalls die alternativen Ausführungs¬ formen von Figur 1 bis 3 zum Blendenkolben 17 übertragbar, so daß die in Figur 4 gezeigte Konstruktion lediglich eine Variante zu den Ausführungsvarianten von Figur 1 bis 3 ver¬ deutlicht. In FIG. 4, the alternative embodiments from FIGS. 1 to 3 can also be transferred to the orifice piston 17, so that the construction shown in FIG. 4 only shows one variant of the embodiment variants from FIGS. 1 to 3.
BezugszeichenlisteReference list
1 Magnetkern1 magnetic core
2 Ventilgehäuse2 valve housings
3 Kammer3 chamber
4 Magnetspule4 solenoid
5 Magnetanker5 magnetic anchors
6 Ventilstößel6 valve lifters
7 Rückstellfeder7 return spring
8 Zwischenteil8 intermediate part
9 Distanzscheibe9 spacer
10 Halteschraube10 retaining screw
11 Ventilschließglied11 valve closing member
12 Hülse12 sleeve
13 Ventilsitz13 valve seat
14 Einlaßkanal14 inlet duct
15 Auslaßkanal15 outlet duct
16 Endlagenteil16 end position part
17 Blendenkolben17 orifice pistons
18 Lancierung18 launch
19 Ringspalt 19 annular gap

Claims

Patentansprüche claims
1. Elektromagnetventil, insbesondere für schlupfgeregelte hydraulische Bremsanlagen, mit einem Ventilgehäuse, das mehrere die Funktion des Elektromagnetventils bestimmte Ventilbauteile, wie ein am Ventilstößel angebrachtes Ventilschließglied und einen Magnetanker aufweist, wobei das Ventilschließglied an einem Ventilsitz sowie der Magnetanker an einem Magnetkern anlegbar sind, mit einer am Magnetkern gehaltenen Hülse, in der der Magnetanker axial beweglich geführt ist, sowie mit einer den Umfang der Hülse umschließenden Magnetspule, die mittels der Schaltstellung des Ventilschließgliedes die Druckmittel¬ verbindung zwischen wenigstens einem Druckmitteleinla߬ kanal und einem Druckmittelauslaßkanal im Ventilgehäuse zu sperren oder zu öffnen vermag, dadurch g e k e n n ¬ z e i c h n e t, daß zwischen dem Magnetanker (5) und der Hülse (12) im Ventilgehäuse (2) ein axial beweg¬ licher Blendenkolben (17) angeordnet ist, der ein Spiel aufweist, welches kleiner ist als das zwischen dem Magnetanker (5) und der Hülse (12) bestehende Spiel.1.Electromagnetic valve, in particular for slip-controlled hydraulic brake systems, with a valve housing which has a plurality of valve components which determine the function of the electromagnetic valve, such as a valve closing member attached to the valve tappet and a magnet armature, the valve closing member being able to be applied to a valve seat and the magnet armature to a magnetic core a sleeve held on the magnetic core, in which the magnet armature is guided in an axially movable manner, and with a magnetic coil surrounding the circumference of the sleeve, which by means of the switching position of the valve closing member block or close the pressure medium connection between at least one pressure medium inlet channel and one pressure medium outlet channel in the valve housing can open, characterized ¬ characterized in that an axially movable diaphragm piston (17) is arranged between the magnet armature (5) and the sleeve (12) in the valve housing (2), which has a play which is smaller than d as between the magnet armature (5) and the sleeve (12) existing game.
2. Elektromagnetventil nach Anspruch 1, dadurch g e ¬ k e n n z e i c h n e t, daß das zwischen dem Blenden¬ kolben (17) und dem Ventilgehäuse (2) bestehende Spiel aus einem Spalt, vorzugsweise einem Ringspalt (19), ge¬ bildet ist.2. Electromagnetic valve according to claim 1, characterized in that the clearance between the diaphragm piston (17) and the valve housing (2) consists of a gap, preferably an annular gap (19), is formed.
3. Elektromagnetventil nach Anspruch 1 oder 2, dadurch g e k e n n z e i c h n e t, daß ein Endlagenteil (16) als im wesentlichen planparallele Platte zum Magnetanker (5) ausgerichtet ist. 3. Solenoid valve according to claim 1 or 2, characterized in that an end position part (16) is aligned as a substantially plane-parallel plate to the armature (5).
4. Elektromagnetventil nach einem der vorhergehenden An¬ sprüche, dadurch g e k e n n z e i c h n e t, daß das Endlagenteil (16) und der Blendenkolben (17) am Magnet¬ anker (5) einen modularen Aufbau aufweisen.4. Solenoid valve according to one of the preceding claims, characterized in that the end position part (16) and the orifice piston (17) on the magnetic armature (5) have a modular structure.
5. Elektromagnetventil nach Anspruch 4, dadurch g e - k e n n z e i c h n e t, daß das Endlagenteil (16) mit der Hülse (12) sowie der Blendenkolben (17) mit dem Magnetanker (5) kraft- und/oder formschlüssige Verbin¬ dungen bilden.5. Solenoid valve according to claim 4, characterized in that the end position part (16) with the sleeve (12) and the orifice piston (17) with the magnet armature (5) form non-positive and / or positive connections.
6. Elektromagnetventil nach Anspruch 5, dadurch g e ¬ k e n n z e i c h n e t, daß die form- und/oder kraft¬ schlüssige Verbindungen mittels Clips oder Halteschrau¬ ben oder als Verstemmung ausgeführt sind.6. Electromagnetic valve according to claim 5, characterized in that the positive and / or non-positive connections are carried out by means of clips or retaining screws or as caulking.
7. Elektromagnetventil nach mindestens einem der vorherge¬ henden Ansprüche 1 bis 6, dadurch g e k e n n ¬ z e i c h n e t, daß der Blendenkolben (17) als Stufen¬ kolben ausgeführt ist, dessen beidseitige Stirnflächen durch Überbrückung eines Wandabstands Endlagenflächen an der gestuften Innenwandung des Ventilgehäuses (2) bilden.7. Solenoid valve according to at least one of the preceding claims 1 to 6, characterized in that the orifice piston (17) is designed as a stepped piston, the end faces of which on both sides by bridging a wall distance, end position surfaces on the stepped inner wall of the valve housing (2) form.
8. Elektromagnetventil nach Anspruch 7, dadurch g e ¬ k e n n z e i c h n e t, daß zwischen dem Blendenkolben (17) und dem Magnetanker (5) eine Distanzscheibe (9) an¬ gebracht ist.8. Solenoid valve according to claim 7, characterized in that a spacer (9) is placed between the orifice piston (17) and the magnet armature (5).
9. Elektromagnetventil nach mindestens einem der vorherge¬ henden Ansprüche 1 bis 6, dadurch g e k e n n ¬ z e i c h n e t, daß ein Endlagenteil (16) diametral zum Magnetanker (5) angeordnet ist, das in der Hülse (12) mittels Lancierung (18) gehalten ist und mit dem der Ventilhub eingestellt ist. 9. Solenoid valve according to at least one of the preceding claims 1 to 6, characterized in that an end position part (16) is arranged diametrically to the magnet armature (5), which is held in the sleeve (12) by means of a launch (18) and with which the valve stroke is set.
PCT/EP1995/000137 1994-03-02 1995-01-13 Electromagnetic valve, in particular for slip-controlled motor vehicle braking systems WO1995023717A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19944406777 DE4406777A1 (en) 1994-03-02 1994-03-02 Solenoid valve, in particular for slip-controlled motor vehicle brake systems
DEP4406777.1 1994-03-02

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Publication Number Publication Date
WO1995023717A1 true WO1995023717A1 (en) 1995-09-08

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WO (1) WO1995023717A1 (en)

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